US20150105218A1 - Method of shifting a transmission - Google Patents
Method of shifting a transmission Download PDFInfo
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- US20150105218A1 US20150105218A1 US14/051,117 US201314051117A US2015105218A1 US 20150105218 A1 US20150105218 A1 US 20150105218A1 US 201314051117 A US201314051117 A US 201314051117A US 2015105218 A1 US2015105218 A1 US 2015105218A1
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 42
- 238000000034 method Methods 0.000 title claims abstract description 21
- 230000010355 oscillation Effects 0.000 claims abstract description 5
- 230000004044 response Effects 0.000 claims description 7
- 230000003247 decreasing effect Effects 0.000 claims description 6
- 230000008859 change Effects 0.000 description 4
- 230000007704 transition Effects 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000001010 compromised effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000003090 exacerbative effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/11—Stepped gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/686—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0444—Smoothing ratio shift during fast shifting over two gearsteps, e.g. jumping from fourth to second gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0451—Smoothing ratio shift during swap-shifts, i.e. gear shifts between different planetary units, e.g. with double transitions shift involving three or more friction members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0455—Smoothing ratio shift during shifts involving three or more shift members, e.g. release of 3-4 clutch, 2-4 brake and apply of forward clutch C1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0462—Smoothing ratio shift by controlling slip rate during gear shift transition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2306/00—Shifting
- F16H2306/40—Shifting activities
- F16H2306/52—Applying torque to new gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
Definitions
- This disclosure relates to the field of automatic transmissions for motor vehicles. More particularly, the disclosure pertains to a method of changing among speed ratios.
- Transmission speed ratio is the ratio of input shaft speed to output shaft speed.
- the transmission is usually operated at a high speed ratio such that it multiplies the engine torque for improved acceleration.
- operating the transmission at a low speed ratio permits an engine speed associated with quiet, fuel efficient cruising.
- an automatic transmission changes from one speed ratio to another speed ratio. For example, when a vehicle is cruising using a low speed ratio and a driver demands an increase in wheel torque, the transmission must downshift into a higher speed ratio. For sudden changes in driver demanded wheel torque, the transmission may skip over one or more available gear ratios in a single shift event.
- Many automatic transmissions have multiple shift elements, such as clutches or brakes, and select particular speed ratios by engaging particular subsets of the shift elements. To perform a shift from one speed ratio to another, one or more previously engaged shift elements are released and one or more previously disengaged shift elements are engaged. Passenger comfort is maximized if the transition is accomplished smoothly. Performance is maximized if the transition is accomplished quickly.
- a method of shifting a transmission includes maintaining a first offgoing element in a fully engaged condition while operating in a first transmission speed ratio, reducing the torque capacity of the first offgoing element during an inertia phase, and then increasing the torque capacity of the first offgoing element at the end of the inertia phase to prevent output shaft oscillation.
- a first oncoming clutch is engaged at the end of the inertia phase. The torque capacity of the first offgoing clutch is then decreased to zero in response to the measured transmission speed ratio decreasing.
- the method may be utilized as part of double transition shift that includes releasing a second offgoing clutch and engaging a second oncoming clutch during the inertia phase.
- the elements may be either brakes or clutches.
- a transmission in another embodiment, includes at least first and second elements and a controller programmed to downshift from a first speed ratio in which the first clutch is engaged to and the second clutch is disengaged to a second speed ratio in which the first clutch is disengaged and the second clutch is engaged by increasing the torque capacity of the first clutch at the end of the inertia phase.
- the transmission may also include a third clutch which is engaged in the first speed ratio and disengaged in the second speed ratio and a fourth clutch that is disengaged in the first speed ratio and engaged in the second speed ratio.
- FIG. 1 is a schematic diagram of an exemplary transmission gearing arrangement.
- FIG. 2 is a graph illustrating speed relationships during execution of a downshift.
- FIG. 3 is a graph illustrating torque relationships during execution of a downshift.
- FIG. 4 is a flowchart illustrating a method of shifting.
- FIG. 1 An example transmission is schematically illustrated in FIG. 1 .
- the transmission utilizes four simple planetary gear sets 20 , 30 , 40 , and 50 .
- Sun gear 26 is fixed to sun gear 36
- carrier 22 is fixed to ring gear 58
- ring gear 38 is fixed to sun gear 46
- ring gear 48 is fixed to sun gear 56
- input shaft 60 is fixed to carrier 32
- output shaft 62 is fixed to carrier 52 .
- Ring gear 28 is selectively held against rotation by brake 66 and sun gears 26 and 36 are selectively held against rotation by brake 68 .
- Input shaft 60 is selectively coupled to ring gear 48 and sun gear 56 by clutch 70 .
- Intermediate shaft 64 is selectively coupled to carrier 42 by clutch 72 , selectively coupled to carrier 22 and ring gear 58 by clutch 74 , and selectively coupled to ring gear 38 and sun gear 46 by clutch 76 .
- All single step and two step shifts are performed by gradually engaging one shift element, called an oncoming element (ONC) while gradually releasing a different shift element, called the offgoing element (OFG).
- ONC oncoming element
- OFG offgoing element
- three shift elements, called holding elements are maintained fully engaged while one shift element is maintained fully disengaged. In other transmission arrangements, the number of holding elements may be different.
- the engine speed must increase to match the new speed ratio.
- the output torque may decrease while some of the power is diverted to increasing engine speed rather than being transmitted to the output. Also, since shift elements are slipping during a shift, some of the power is converted to heat, exacerbating the output torque deficiency.
- the shift scheduling algorithm may demand a multiple step downshift.
- two shift elements must be releases and two shift elements must be engaged.
- brake 68 (OFG 1 ) and clutch 76 (OFG 2 ) must be released and clutch 70 (ONC 1 ) and brake 66 (ONC 2 ) must be engaged.
- FIGS. 2 and 3 illustrate speed and torque relationships for a shift from 10th gear to 6th gear in the transmission of FIG. 1 .
- Line 60 in FIG. 2 shows the input speed as a function of time assuming that output speed is substantially constant. The remaining lines depict the relative speeds across various clutches and brakes. The scale is not necessarily identical among lines.
- Line 62 in FIG. 3 shows the output torque as a function of time assuming that input torque is substantially constant. The remaining lines depict the torque transmitted by various clutches and brakes. Again, the scale is not necessarily identical among these lines.
- FIG. 4 is a flow diagram illustrating a method of controlling shift elements to effectuate a shift such as the shift illustrated in FIGS. 2 and 3 .
- the downshift is initiated at 122 in FIG. 4 by gradually reducing the commanded torque capacity of brake 68 (OFG 1 ) as shown between 84 and 86 in FIG. 3 .
- brake 68 When the torque capacity becomes less than the capacity required to maintain 10th gear, brake 68 will begin to slip and input speed will begin to rise marking the beginning of the inertia phase. As shown by line 62 in FIG. 3 , the output torque drops during this phase as power is diverted to increasing engine speed.
- the torque capacity of brake 68 (OFG 1 ) determines how much the output torque drops and how quickly the engine speed increases as shown at 124 in FIG. 4 . If the torque capacity of brake 68 is close to zero, then very little of the engine power will be transmitted to the output but the engine speed will increase rapidly. On the other hand, if the torque capacity of brake 68 is maintained close to the level that brake 68 would transmit in 10th gear, then most of the engine power will be transmitted to the output shaft and engine speed will increase slowly.
- the torque capacity of brake 68 is increased at a calibratable rate between 92 and 94 in FIG. 3 and at 136 in FIG. 4 .
- the torque capacity of brake 68 is decreased at a calibratable rate as shown between 102 and 104 in FIG. 3 and at 140 in FIG. 4 .
- Point 102 may also be determined by a change in direction of the relative speed across either offgoing shift element 68 or 76 or of the second oncoming shift element 66 .
- brake 68 absorbs energy, dampening any oscillation and resulting in the smooth torque transition illustrated at 106 in FIG. 3 .
Abstract
Description
- This disclosure relates to the field of automatic transmissions for motor vehicles. More particularly, the disclosure pertains to a method of changing among speed ratios.
- Many vehicles are used over a wide range of vehicle speeds, including both forward and reverse movement. Some types of engines, however, are capable of operating efficiently only within a narrow range of speeds. Consequently, transmissions capable of efficiently transmitting power at a variety of speed ratios are frequently employed. Transmission speed ratio is the ratio of input shaft speed to output shaft speed. When the vehicle is at low speed, the transmission is usually operated at a high speed ratio such that it multiplies the engine torque for improved acceleration. At high vehicle speed, operating the transmission at a low speed ratio permits an engine speed associated with quiet, fuel efficient cruising.
- When driving conditions change, an automatic transmission changes from one speed ratio to another speed ratio. For example, when a vehicle is cruising using a low speed ratio and a driver demands an increase in wheel torque, the transmission must downshift into a higher speed ratio. For sudden changes in driver demanded wheel torque, the transmission may skip over one or more available gear ratios in a single shift event. Many automatic transmissions have multiple shift elements, such as clutches or brakes, and select particular speed ratios by engaging particular subsets of the shift elements. To perform a shift from one speed ratio to another, one or more previously engaged shift elements are released and one or more previously disengaged shift elements are engaged. Passenger comfort is maximized if the transition is accomplished smoothly. Performance is maximized if the transition is accomplished quickly. These considerations are often in conflict.
- A method of shifting a transmission includes maintaining a first offgoing element in a fully engaged condition while operating in a first transmission speed ratio, reducing the torque capacity of the first offgoing element during an inertia phase, and then increasing the torque capacity of the first offgoing element at the end of the inertia phase to prevent output shaft oscillation. A first oncoming clutch is engaged at the end of the inertia phase. The torque capacity of the first offgoing clutch is then decreased to zero in response to the measured transmission speed ratio decreasing. The method may be utilized as part of double transition shift that includes releasing a second offgoing clutch and engaging a second oncoming clutch during the inertia phase. The elements may be either brakes or clutches.
- In another embodiment, a transmission includes at least first and second elements and a controller programmed to downshift from a first speed ratio in which the first clutch is engaged to and the second clutch is disengaged to a second speed ratio in which the first clutch is disengaged and the second clutch is engaged by increasing the torque capacity of the first clutch at the end of the inertia phase. The transmission may also include a third clutch which is engaged in the first speed ratio and disengaged in the second speed ratio and a fourth clutch that is disengaged in the first speed ratio and engaged in the second speed ratio.
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FIG. 1 is a schematic diagram of an exemplary transmission gearing arrangement. -
FIG. 2 is a graph illustrating speed relationships during execution of a downshift. -
FIG. 3 is a graph illustrating torque relationships during execution of a downshift. -
FIG. 4 is a flowchart illustrating a method of shifting. - Embodiments of the present disclosure are described herein. It is to be understood, however, that the disclosed embodiments are merely examples and other embodiments can take various and alternative forms. The figures are not necessarily to scale; some features could be exaggerated or minimized to show details of particular components. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching one skilled in the art to variously employ the present invention. As those of ordinary skill in the art will understand, various features illustrated and described with reference to any one of the figures can be combined with features illustrated in one or more other figures to produce embodiments that are not explicitly illustrated or described. The combinations of features illustrated provide representative embodiments for typical applications. Various combinations and modifications of the features consistent with the teachings of this disclosure, however, could be desired for particular applications or implementations.
- An example transmission is schematically illustrated in
FIG. 1 . The transmission utilizes four simpleplanetary gear sets gear 26 is fixed tosun gear 36,carrier 22 is fixed toring gear 58,ring gear 38 is fixed tosun gear 46,ring gear 48 is fixed tosun gear 56,input shaft 60 is fixed tocarrier 32, andoutput shaft 62 is fixed tocarrier 52.Ring gear 28 is selectively held against rotation bybrake 66 andsun gears brake 68.Input shaft 60 is selectively coupled toring gear 48 andsun gear 56 byclutch 70.Intermediate shaft 64 is selectively coupled tocarrier 42 byclutch 72, selectively coupled tocarrier 22 andring gear 58 byclutch 74, and selectively coupled toring gear 38 andsun gear 46 byclutch 76. - As shown in Table 1, engaging the clutches and brakes in combinations of four establishes ten forward speed ratios and one reverse speed ratio between
input shaft 60 andoutput shaft 62. An X indicates that the corresponding shift element is engaged to establish the speed ratio. -
TABLE 1 66 68 70 72 74 76 Ratio Step Rev X X X X −4.79 102% 1st X X X X 4.70 2nd X X X X 2.99 1.57 3rd X X X X 2.18 1.37 4th X X X X 1.80 1.21 5th X X X X 1.54 1.17 6th X X X X 1.29 1.19 7th X X X X 1.00 1.29 8th X X X X 0.85 1.17 9th X X X X 0.69 1.24 10th X X X X 0.64 1.08 - All single step and two step shifts are performed by gradually engaging one shift element, called an oncoming element (ONC) while gradually releasing a different shift element, called the offgoing element (OFG). During each of these shifts, three shift elements, called holding elements, are maintained fully engaged while one shift element is maintained fully disengaged. In other transmission arrangements, the number of holding elements may be different.
- During a downshift, the engine speed must increase to match the new speed ratio. The output torque may decrease while some of the power is diverted to increasing engine speed rather than being transmitted to the output. Also, since shift elements are slipping during a shift, some of the power is converted to heat, exacerbating the output torque deficiency.
- Sometimes, it is desirable to downshift by more than two ratio steps. For example, if the vehicle driver presses the accelerator pedal to pass another vehicle while cruising on the highway in top gear, the shift scheduling algorithm may demand a multiple step downshift. For some multiple step downshifts, two shift elements must be releases and two shift elements must be engaged. For example, to shift from 10th gear in the example transmission to 6th gear in the example transmission, brake 68 (OFG1) and clutch 76 (OFG2) must be released and clutch 70 (ONC1) and brake 66 (ONC2) must be engaged. While it is possible to complete such a shift in two stages, by shifting temporarily into 8th gear for example, completing the shift in that manner would require more time and result in more output torque disturbance than making the shift in a single process. Fluctuating output torque tends to be annoying to the driver as it translates directly into fluctuating vehicle acceleration.
-
FIGS. 2 and 3 illustrate speed and torque relationships for a shift from 10th gear to 6th gear in the transmission ofFIG. 1 .Line 60 inFIG. 2 shows the input speed as a function of time assuming that output speed is substantially constant. The remaining lines depict the relative speeds across various clutches and brakes. The scale is not necessarily identical among lines.Line 62 inFIG. 3 shows the output torque as a function of time assuming that input torque is substantially constant. The remaining lines depict the torque transmitted by various clutches and brakes. Again, the scale is not necessarily identical among these lines.FIG. 4 is a flow diagram illustrating a method of controlling shift elements to effectuate a shift such as the shift illustrated inFIGS. 2 and 3 . - The downshift is initiated at 122 in
FIG. 4 by gradually reducing the commanded torque capacity of brake 68 (OFG1) as shown between 84 and 86 inFIG. 3 . When the torque capacity becomes less than the capacity required to maintain 10th gear,brake 68 will begin to slip and input speed will begin to rise marking the beginning of the inertia phase. As shown byline 62 inFIG. 3 , the output torque drops during this phase as power is diverted to increasing engine speed. The torque capacity of brake 68 (OFG1) determines how much the output torque drops and how quickly the engine speed increases as shown at 124 inFIG. 4 . If the torque capacity ofbrake 68 is close to zero, then very little of the engine power will be transmitted to the output but the engine speed will increase rapidly. On the other hand, if the torque capacity ofbrake 68 is maintained close to the level that brake 68 would transmit in 10th gear, then most of the engine power will be transmitted to the output shaft and engine speed will increase slowly. - As shown in
FIG. 2 , as the input shaft increases in speed, the speed difference across clutch 70 (ONC1) and brake 66 (ONC2) decrease. During this period, the pressure supplied to clutch 70 andbrake 66 may be increased in order to prepare for later engagement, but not enough to exert substantial torque. When the speed difference across clutch 70 (ONC1) reaches zero at 88 inFIG. 2 and at 126 inFIG. 4 , the torque capacity of clutch 76 (OFG2) is rapidly ramped to zero and the torque capacity of clutch 70 (ONC1) is rapidly increased as shown at 128 inFIG. 4 . The torque capacity of brake 66 (OFG1) continues to control the rate of change of the input speed as shown at 130 inFIG. 4 . - When the speed difference across brake 66 (ONC2) reaches zero at 90 in
FIG. 2 and at 132 inFIG. 4 , the inertia phase ends and the torque phase begins. The torque capacity of brake 66 (ONC2) is rapidly increased between 92 and 94 inFIG. 3 and at 134 inFIG. 4 . Engagingbrake 66 beforepoint 92 would cause a further reduction in output torque. Becausebrake 66 does not immediately reach sufficient torque capacity to stopring gear 28, the direction of rotation ofbrake 66 may briefly change as shown at 96 inFIG. 2 . As shown at 98 inFIG. 2 , the input speed may also temporarily exceed the speed associated with the final gear ratio. Asbrake 66 pulls the input speed back down to it final value, excess energy in various transmission components can result in windup in various shafts such as the vehicle driveshaft. Unless action is taken to dissipate this energy, the output shaft will oscillate as shown by the dotted lines at 100. - Instead of immediately releasing brake 68 (OFG1), the torque capacity of
brake 68 is increased at a calibratable rate between 92 and 94 inFIG. 3 and at 136 inFIG. 4 . When the input speed begins to decrease at 98 inFIG. 2 and at 138 inFIG. 4 , the torque capacity ofbrake 68 is decreased at a calibratable rate as shown between 102 and 104 inFIG. 3 and at 140 inFIG. 4 .Point 102 may also be determined by a change in direction of the relative speed across eitheroffgoing shift element oncoming shift element 66. Betweenpoints brake 68 absorbs energy, dampening any oscillation and resulting in the smooth torque transition illustrated at 106 inFIG. 3 . - While exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms encompassed by the claims. The words used in the specification are words of description rather than limitation, and it is understood that various changes can be made without departing from the spirit and scope of the disclosure. As previously described, the features of various embodiments can be combined to form further embodiments of the invention that may not be explicitly described or illustrated. While various embodiments could have been described as providing advantages or being preferred over other embodiments or prior art implementations with respect to one or more desired characteristics, those of ordinary skill in the art recognize that one or more features or characteristics can be compromised to achieve desired overall system attributes, which depend on the specific application and implementation. These attributes can include, but are not limited to cost, strength, durability, life cycle cost, marketability, appearance, packaging, size, serviceability, weight, manufacturability, ease of assembly, etc. As such, embodiments described as less desirable than other embodiments or prior art implementations with respect to one or more characteristics are not outside the scope of the disclosure and can be desirable for particular applications.
Claims (14)
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US14/051,117 US9308908B2 (en) | 2013-10-10 | 2013-10-10 | Method of shifting a transmission |
CN201410476840.5A CN104565350B (en) | 2013-10-10 | 2014-09-18 | Make the method for shifting of transmission |
DE102014220004.0A DE102014220004B4 (en) | 2013-10-10 | 2014-10-02 | Method of shifting a transmission |
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US14/051,117 US9308908B2 (en) | 2013-10-10 | 2013-10-10 | Method of shifting a transmission |
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US20150105218A1 true US20150105218A1 (en) | 2015-04-16 |
US9308908B2 US9308908B2 (en) | 2016-04-12 |
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US20170198808A1 (en) * | 2016-01-11 | 2017-07-13 | Cnh Industrial America Llc | System and method for controlling a powershift transmission |
US10145467B2 (en) * | 2016-03-15 | 2018-12-04 | Honda Motor Co., Ltd. | Automatic transmission |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6565954B2 (en) * | 2017-02-16 | 2019-08-28 | トヨタ自動車株式会社 | Vehicle control device |
US10344851B2 (en) * | 2017-06-27 | 2019-07-09 | Ford Global Technologies, Llc | Method of controlling a transmission during an upshift |
US11414081B1 (en) * | 2021-02-04 | 2022-08-16 | Ford Global Technologies, Llc | Predictive-based control for transmission shifting |
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2013
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US20170198808A1 (en) * | 2016-01-11 | 2017-07-13 | Cnh Industrial America Llc | System and method for controlling a powershift transmission |
US10227942B2 (en) * | 2016-01-11 | 2019-03-12 | Cnh Industrial America Llc | System and method for controlling a powershift transmission |
US10145467B2 (en) * | 2016-03-15 | 2018-12-04 | Honda Motor Co., Ltd. | Automatic transmission |
Also Published As
Publication number | Publication date |
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DE102014220004A1 (en) | 2015-04-16 |
US9308908B2 (en) | 2016-04-12 |
DE102014220004B4 (en) | 2022-03-31 |
CN104565350A (en) | 2015-04-29 |
CN104565350B (en) | 2018-04-17 |
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